US20110112724A1

US20110112724A1 - Motor control unit and vehicle steering system

Info

Publication number: US20110112724A1
Application number: US12/945,101
Authority: US
Inventors: Yuji Kariatsumari; Terutaka Tamaizumi; Yoshinobu Shimizu
Original assignee: JTEKT Corp
Current assignee: JTEKT Corp
Priority date: 2009-11-12
Filing date: 2010-11-12
Publication date: 2011-05-12
Also published as: EP2323250A3; EP2323250B1; EP2323250A2; JP2011109733A; JP5532295B2; US8855858B2

Abstract

A motor control unit includes a detected steering torque correction unit that corrects the detected steering torque that is detected by a torque sensor and then subjected to a limitation process by a steering torque limiter. When the absolute value of the detected steering torque is equal to or smaller than a predetermined value, the detected steering torque correction unit corrects the detected steering torque to 0. When the absolute value of the detected steering torque is larger than the predetermined value, the detected steering torque correction unit outputs the detected steering torque without correction. A PI control unit calculates the addition angle based on the deviation of the control torque obtained through correction by the detected steering torque correction unit from the command steering torque.

Description

INCORPORATION BY REFERENCE

The disclosure of Japanese Patent Application No. 2009-258962 filed on Nov. 12, 2009 including the specification, drawings and abstract is incorporated herein by reference in its entirety.

BACKGROUND OF THE INVENTION

1. Field of the Invention
The invention relates to a motor control unit used to drive a brushless motor, and a vehicle steering system, for example, an electric power steering system, which includes the motor control unit.
2. Description of the Related Art
A motor control unit that controls driving of a brushless motor is usually configured to control the electric current that is supplied to a motor based on the output from a rotational angle sensor that detects the rotational angle of a rotor. As a rotational angle sensor, a resolver that outputs a sine-wave signal and a cosine-wave signal that correspond to the rotational angle (electrical angle) of a rotor is usually used. However, a resolver is expensive, and needs a large number of wires and a large installation space. Therefore, using a resolver as a rotational angle sensor hinders reduction in cost and size of a unit that includes a brushless motor.
To address this problem, a sensorless drive method for driving a brushless motor without using a rotational angle sensor has been proposed. According to the sensorless drive method, the induced voltage that is caused due to the rotation of a rotor is estimated in order to estimate the phase of a magnetic pole (electrical angle of the rotor). When the rotor is at a standstill or rotating at a considerably low speed, it is not possible to estimate the phase of the magnetic pole. Therefore, the phase of the magnetic pole is estimated by another method. More specifically, a sensing signal is input in a stator, and a response of the motor to the sensing signal is detected. Then, the rotational position of the rotor is estimated based on the response of the motor.
For example, Japanese Patent Application Publication No. 10-243699 (JP-A-10-243699) describes the related art.
According to the sensorless drive method described above, the rotational position of the rotor is estimated based on the induced voltage or the sensing signal, and the motor is controlled based on the estimated rotational position. However, this drive method is not suitable for all uses. There has not been established a method suitable for a control of a brushless motor that is used as a drive source for, for example, a vehicle steering system such as an electric power steering system that supplies a steering assist force to a vehicle steering mechanism. Accordingly, a sensorless control executed by another method has been demanded.

SUMMARY OF INVENTION

The invention provides a motor control unit that controls a motor according to a new control method that does not require a rotational angle sensor, and a vehicle steering system that includes the motor control unit.
A first aspect of the invention relates to a motor control unit that controls a motor that includes a rotor and a stator that faces the rotor. The motor control unit includes a current drive unit, an addition angle calculation unit, a control angle calculation unit, a control torque calculation unit, and a command torque setting unit. The current drive unit drives the motor based on an axis current value of a rotating coordinate system that rotates in accordance with a control angle that is a rotational angle used in a control. The addition angle calculation unit calculates an addition angle that should be added to the control angle. The control angle calculation unit obtains a present value of the control angle by adding the addition angle calculated by the addition angle calculation unit to an immediately preceding value of the control angle in predetermined calculation cycles. The control torque calculation unit calculates a control torque based on a torque that is other than a motor torque and that is applied to a drive target that is driven by the motor. The command torque setting unit sets a command torque that is a torque that is other than the motor torque and that should be applied to the drive target. The addition angle calculation unit calculates the addition angle based on the deviation of the control torque calculated by the control torque calculation unit from the command torque set by the command torque setting unit.

BRIEF DESCRIPTION OF DRAWINGS

The foregoing and further objects, features and advantages of the invention will become apparent from the following description of example embodiments with reference to the accompanying drawings, wherein like numerals are used to represent like elements and wherein:

FIG. 1 is a block diagram for describing the electrical configuration of an electric power steering system to which a motor control unit according to an embodiment of the invention is applied;

FIG. 2 is a view for describing the configuration of a motor;

FIG. 3 is a control block diagram for the electric power steering system;

FIG. 4 is a graph showing an example of the characteristic of the command steering torque with respect to the steering angle;

FIG. 5 is a graph for describing the function of a steering torque limiter;

FIG. 6 is a graph for describing the function of a detected steering torque correction unit;

FIG. 7 is a graph showing an example of a manner of setting the g-axis command current value;

FIG. 8 is a flowchart for describing the function of an addition angle limiter;

FIG. 9 is a graph for describing the function of a detected steering torque correction unit according to another embodiment; and

FIG. 10 is a graph for describing the function of a detected steering torque correction unit according to another embodiment.

DETAILED DESCRIPTION OF EXAMPLE EMBODIMENTS

Hereafter, example embodiments of the invention will be described in detail with reference to the accompanying drawings. FIG. 1 is a block diagram for describing the electrical configuration of an electric power steering system (an example of a vehicle steering system) to which a motor control unit according to an embodiment of the invention is applied. The electric power steering system includes a torque sensor 1, a motor 3 (brushless motor), a steering angle sensor 4, a motor control unit 5, and a vehicle speed sensor 6. The torque sensor 1 detects the steering torque T that is applied to a steering wheel 10 that serves as an operation member used to steer a vehicle. The motor 3 (brushless motor) applies a steering assist force to a steering mechanism 2 of the vehicle via a speed reduction mechanism 7. The steering angle sensor 4 detects the steering angle that is the rotational angle of the steering wheel 10. The motor control unit 5 controls driving of the motor 3. The vehicle speed sensor 6 detects the speed of the vehicle in which the electric power steering system is mounted. The steering angle sensor 4 detects the amount of rotation (rotational angle) of the steering wheel 10 from the neutral position (reference position) of the steering wheel 10 in the clockwise direction, and the amount of rotation of the steering wheel 10 from the neutral position in the counterclockwise direction. The steering angle sensor 4 outputs, as a positive value, the amount of rotation of the steering wheel 10 from the neutral position in the clockwise direction. The steering angle sensor outputs, as a negative value, the amount of rotation of the steering wheel 10 from the neutral position in the counterclockwise direction.
The motor control unit 5 drives the motor 3 based on the steering torque detected by the torque sensor 1, the steering angle detected by the steering angle sensor 4, and the vehicle speed detected by the vehicle speed sensor 6, thereby providing appropriate steering assistance based on the steering state and the vehicle speed.
In the embodiment, the motor 3 is a three-phase brushless motor. As illustrated in FIG. 2, the motor 3 includes a rotor 50 that serves as a field magnet, and a U-phase stator coil 51, a V-phase stator coil 52, and a W-phase stator coil 53 that are arranged on a stator 55 that faces the rotor 50. The motor 3 may be an inner rotor motor in which a stator is arranged on the outer side of a rotor so as to face the rotor, or an outer rotor motor in which a stator is arranged on the inner side of a tubular rotor so as to face the rotor.
A three-phase fixed coordinate system (UVW coordinate system), where the direction in which the U-phase stator coil 51 extends, the direction in which the V-phase coil 52 extends, and the direction in which the W-phase coil 53 extends are used as the U-axis, the V-axis and W-axis, respectively, is defined. In addition, a two-phase rotating coordinate system (dq coordinate system: actual rotating coordinate system), where the direction of the magnetic poles of the rotor 50 is used as the d-axis (axis of the magnetic poles) and the direction that is perpendicular to the d-axis within the rotary plane of the rotor 50 is used as the q-axis (torque axis), is defined. The dq coordinate system is a rotating coordinate system that rotates together with the rotor 50. In the dq coordinate system, only the q-axis current contributes to generation of torque by the rotor 50. Therefore, the d-axis current may be set to 0 and the q-axis current may be controlled based on a desired torque. The rotational angle (rotor angle) θ_Mof the rotor 50 is a rotational angle of the d-axis with respect to the U-axis. The dq coordinate system is an actual rotating coordinate system that rotates in accordance with the rotor angle θ_M. With the use of the rotor angle θ_M, coordinate conversion may be made between the UVW coordinate system and the dq coordinate system.
In the embodiment, the control angle θ_Cthat indicates the rotational angle used in the control is employed. The control angle θ_Cis an imaginary rotational angle with respect to the U-axis. An imaginary two-phase rotating coordinate system (γδ coordinate system: hereafter, referred to as “imaginary rotating coordinate system”), where the imaginary axis that forms the control angle θ_Cwith the U-axis is used as the γ-axis, and the axis that is advanced 90 degrees from the γ-axis is used as the δ-axis, is defined. When the control angle θ_Cis equal to the rotor angle θ_M, the γδ coordinate system, which is the imaginary rotating coordinate system, and the dq coordinate system, which is the actual rotating coordinate system, coincide with each other. That is, the γ-axis, which is the imaginary axis, coincides with the d-axis, which is the actual axis, and the δ-axis, which is the imaginary axis, coincides with the q-axis, which is the actual axis. The γδ coordinate system is an imaginary rotating coordinate system that rotates in accordance with the control angle θ_C. Coordinate conversion may be made between the UVW coordinate system and the γδ coordinate system with the use of the control angle θ_C.
The load angle θ_L(=θ_C−θ_M) is defined based on the difference between the control angle θ_Cand the rotor angle θ_M. When the γ-axis current I_γ is supplied to the motor 3 based on the control angle θ_C, the q-axis component of the γ-axis current I_γ (orthogonal projection to the q-axis) is used as the q-axis current I_qthat contributes to generation of torque by the rotor 50. That is, the relationship expressed by Equation 1 is established between the γ-axis current I_γ and the q-axis current I_q.
I _q =I _γ×sin θ_L Equation 1
Referring again to FIG. 1, the motor control unit 5 includes a microcomputer 11, a drive circuit (inverter circuit) 12 that is controlled by the microcomputer 11 and that supplies electric power to the motor 3, and a current detection unit 13 that detects an electric current that flows through the stator coil of each phase of the motor 3.
The current detection unit 13 detects the U-phase current I_U, the V-phase current I_Vand the W-phase current I_Wthat flow through the U-phase stator coil 51, the V-phase stator coil 52, and the W-phase stator coil 53 of the motor 3, respectively, (these phase currents will be collectively referred to as “three-phase detected current I_UVW” where appropriate). The U-phase current I_U, the V-phase current I_Vand the W-phase current I_Ware the current values in the directions of the axes of the UVW coordinate system. The microcomputer 11 includes a CPU and memories (a ROM, a RAM, etc.), and serves as multiple function processing units by executing predetermined programs. The multiple function processing units include a steering torque limiter 20, a command steering torque setting unit 21, a torque deviation calculation unit 22, a PI (proportional-integral) control unit 23, an addition angle limiter 24, a control angle calculation unit 26, a command current value preparation unit 30, a current deviation calculation unit 32, a PI control unit 33, a γδ/UVW conversion unit 34, a PWM (Pulse Width Modulation) control unit 35, a UVW/γδ conversion unit 36, and a detected steering torque correction unit 40.
The command steering torque setting unit 21 sets the command steering torque T* based on the steering angle detected by the steering angle sensor 4 and the vehicle speed detected by the vehicle speed sensor 6. For example, as shown in FIG. 4, the command steering torque T* when the steering angle is a positive value (when the steering wheel 10 is operated clockwise) is set to a positive value (torque applied in the clockwise direction), whereas the command steering torque T* when the steering angle is a negative value (when the steering wheel 10 is operated counterclockwise) is set to a negative value (torque applied in the counterclockwise direction). The command steering torque T* is set in such a manner that the absolute value of the command steering torque T* increases (non-linearly increases, in the example in FIG. 4) as the absolute value of the steering angle increases. However, the command steering torque T* is set to a value within a range between a predetermined upper limit (positive value (e.g. +6Nm)) and a predetermined lower limit (negative value (e.g. −6Nm)). In addition, the command steering torque T* is set in such a manner that the absolute value of the command steering torque T* decreases as the vehicle speed increases. That is, a vehicle speed-sensitive control is executed.
The steering torque limiter 20 limits the output from the torque sensor 1 within a range between a predetermined upper saturation value +T_max(+T_max>0 (e.g. +T_max=7 Nm)) and a predetermined lower saturation value −T_max(−T_max<0 (e.g. −T_max=−7 Nm)). More specifically, as shown in FIG. 5, when the output from the torque sensor 1 is within the range between the upper saturation value +T_maxand the lower saturation value −T_max, the steering torque limiter 20 outputs the detected steering torque that is the value output from the torque sensor 1 without limitation. When the detected steering torque from the torque sensor 1 is equal to or higher than the upper saturation value +T_max, the steering torque limiter 20 outputs the upper saturation value +T_max. When the detected steering torque from the torque sensor 1 is equal to or lower than the lower saturation value −T_max, the steering torque limiter 20 outputs the lower saturation value −T_max. The saturation values +T_maxand −T_maxdefine a stable range (reliable range) of the output signal from the torque sensor 1. That is, in the range where the output from the torque sensor 1 is higher than the upper saturation value +T_maxand the range where the output from the torque sensor 1 is lower than the lower saturation value −T_max, the output signal from the torque sensor 1 is unstable and does not correspond to the actual steering torque. In other words, the saturation values +T_maxand −T_maxare determined based on the output characteristic of the torque sensor 1. Hereafter, the steering torque that is detected by the torque sensor 1 and then subjected to the limitation process by the steering torque limiter 20 will be referred to as “detected steering torque T_L”.
The detected steering torque correction unit 40 is a control torque calculation unit that calculates the control detected steering torque based on the detected steering torque T_Lobtained by the steering torque limiter 20. In other words, the detected steering torque correction unit 40 prepares the control detected steering torque (hereinafter, simply referred to as “control torque T”) by correcting the detected steering torque T_L. More specifically, when the absolute value |T_L| of the detected steering torque T_Lis equal to or smaller than the predetermined value a (a>0) (|T_L|≦a), the detected steering torque correction unit 40 corrects the detected steering torque to 0, as shown in FIG. 6. On the other hand, when the absolute value |T_L| of the detected steering torque T_Lis larger than the predetermined value a (|T_L|>a), the detected steering torque correction unit 40 outputs the detected steering torque T_Lwithout correction. The predetermined value a is set to, for example, a value within a range from 0.3 Nm to 0.5 Nm. The control torque T after correction made by the detected steering torque correction unit 40 is expressed by Equation 2.
If |T _L |≦a, T=0
If |T _L |>a, T=T _L Equation 2
The torque deviation calculation unit 22 obtains the deviation (torque deviation) ΔT (=T*−T) of the control torque T, which is detected by the torque sensor 1 and then subjected to the limitation process executed by the torque limiter 20 and the correction executed by the detected steering torque correction unit 40, from the command steering torque T* that is set by the command steering torque setting unit 21. The PI control unit 23 executes the PI calculation on the torque deviation ΔT. That is, the torque deviation calculation unit 22 and the PI control unit 23 constitute a torque feedback control unit that brings the control torque T to the command steering torque T*. The PI control unit 23 calculates the addition angle α for the control angle θ_Cby executing the PI calculation on the torque deviation ΔT. Therefore, the torque feedback control unit constitutes an addition angle calculation unit that calculates the addition angle α that should be added to the control angle θ_C.
The addition angle limiter 24 imposes limits on the addition angle α obtained by the PI control unit 23. More specifically, the addition angle limiter 24 limits the addition angle α to a value within a range between a predetermined upper limit UL (positive value) and a predetermined lower limit LL (negative value). The upper limit UL and the lower limit LL are determined based on a predetermined limit ω_max(ω_max>0: e.g. preset value of ω_max=45 degrees). The preset value of the predetermined limit ω_maxis determined based on, for example, the maximum steering angular speed. The maximum steering angular speed is the maximum assumable value of the steering angular speed of the steering wheel 10, and, for example, approximately 800 deg/sec.
The rate of change in the electrical angle of the rotor 50 (angular speed in the electrical angle: maximum rotor angular speed) at the maximum steering angular speed is expressed by the product of the maximum steering angular speed, the speed reduction ratio of the speed reduction mechanism 7, and the number of pole pairs of the rotor 50, as indicated by Equation 3. The number of pole pairs is the number of magnetic pole pairs (pair of north pole and south pole) of the rotor 50.
Maximum rotor angular speed=maximum steering angular speed×speed reduction ratio×number of pole pairs Equation 3
The maximum value of the amount of change in the electrical angle of the rotor 50 between the calculations (in the calculation cycle) of the control angle θ_Cis expressed by the value obtained by multiplying the maximum rotor angular speed by the calculation cycle, as indicated by Equation 4.
Maximum value of amount of change in rotor angle=maximum rotor angular speed×calculation cycle=maximum steering angular speed×speed reduction ratio×number of pole pairs×calculation cycle Equation 4
This maximum value of the amount of change in the rotor angle is the maximum amount of change in the control angle θ_Cthat is permitted within one calculation cycle. Therefore, the maximum value of the amount of change in the rotor angle may be used as the preset value of the limit ω_max. With the use of the limit ω_max, the upper limit UL and the lower limit LL for the addition angle α are expressed by Equation 5 and Equation 6, respectively.
UL=+ω_max Equation 5
LL=−ω_max Equation 6
The addition angle α obtained after the above-described limitation process executed by the addition angle limiter 24 is added to the immediately preceding value θ_C(n−1) (n is the number of the present calculation cycle) of the control angle θ_Cby an addition unit 26A of the control angle calculation unit 26 (“Z⁻¹” in the drawings indicates the immediately preceding value indicated by a signal). Note that, the initial value of the control angle θ_Cis a predetermined value (e.g. 0).
The control angle calculation unit 26 includes the addition unit 26A that adds the addition angle α provided from the addition angle limiter 24 to the immediately preceding value θ_C(n−1) of the control angle θ_C. That is, the control angle calculation unit 26 calculates the control angle θ_Cin predetermined calculation cycles. The control angle calculation unit 26 uses the control angle θ_Cin the immediately preceding calculation cycle as the immediately preceding value θ_C(n−1), and obtains the present value θ_C(n) that is the control angle θ_Cin the present calculation cycle based on the immediately preceding value θ_C(n−1). The command current value preparation unit 30 prepares, as command current values, values of electric currents that should be supplied to the coordinate axes (imaginary axes) of the γδ coordinate system, which is the imaginary rotating coordinate system that corresponds to the control angle θ_Cthat is a rotational angle used in the control. More specifically, the command current value preparation unit 30 prepares the γ-axis command current value I_γ* and the δ-axis command current value I_δ* (hereinafter, these values will be collectively referred to as “two-phase command current value I_γδ*” where appropriate). The command current value preparation unit 30 sets the γ-axis command current value I_γ* to a significant value, and sets the δ-axis command current value I_δ* to 0. More specifically, the command current value preparation unit 30 sets the γ-axis command current value I_γ* based on the detected steering torque T_Lthat is detected by the torque sensor 1 and then subjected to the limitation process executed by the steering torque limiter 20.
FIG. 7 shows an example of a manner of setting the γ-axis command current value I_γ* with respect to the detected steering torque T_L. The γ-axis command current value I_γ* is set to a low value within a range L where the detected steering torque T_Lis near 0. The γ-axis command current value I_γ* rises sharply in the region outside the range L where the detected steering torque T_Lis near 0, and is maintained substantially constant in the region where the torque is at or higher than a predetermined value. Thus, when the driver does not operate the steering wheel 10, the γ-axis command current value I_γ* is reduced to suppress unnecessary electric power consumption.
The current deviation calculation unit 32 calculates the deviation I_γ*−I_γ of the γ-axis detected current I_γ from the γ-axis command current value I_γ* prepared by the command current value preparation unit 30, and the deviation I_δ*−I_δ of the δ-axis detected current I_δ from the δ-axis command current value I_δ*(=0). The γ-axis detected current I_γ and the δ-axis detected current I_δ are provided from the UVW/γδ conversion unit 36 to the deviation calculation unit 32.
The UVW/γδ conversion unit 36 converts the three-phase detected current I_UVW(U-phase detected current I_U, V-phase detected current I_V, and the W-phase detected current I_W) of the UVW coordinate system, which is detected by the current detection unit 13, into the two-phase detected currents I_γ and I_δ of the γδ coordinate system (hereinafter, these phase currents will be collectively referred to as “two-phase detected current I_γδ” where appropriate). These two-phase detected currents I_γ and I_δ are provided to the current deviation calculation unit 32. The control angle θ_Ccalculated by the control angle calculation unit 26 is used for the coordinate conversion that is executed by the UVW/γδ conversion unit 36.
The PI control unit 33 executes the PI calculation on the current deviation calculated by the current deviation calculation unit 32 to prepare the two-phase command voltage V_γδ*(the γ-axis command voltage V_γ* and the δ-axis command voltage V_δ*) that should be applied to the motor 3. The two-phase command voltage V_γδ* is provided to the γδ/UVW conversion unit 34. The γδ/UVW conversion unit 34 executes the coordinate conversion calculation on the two-phase command voltage V_γδ* to prepare the three-phase command voltage V_UVW*. The three-phase command voltage V_UVW* is formed of the U-phase command voltage V_U*, the V-phase command voltage V_V* and the W-phase command voltage V_W*. The three-phase command voltage V_UVW* is provided to the PWM control unit 35.
The PWM control unit 35 prepares the U-phase PWM control signal, the V-phase PWM control signal and the W-phase PWM control signal having duty ratios that correspond to the U-phase command voltage V_U*, the V-phase command voltage V_V* and the W-phase command voltage V_W*, respectively, and provides the control signals to the drive circuit 12. The drive circuit 12 is formed of an inverter circuit having three phases that correspond to the U-phase, the V-phase and the W-phase. The power elements that constitute the inverter circuit are controlled based on the PWM control signals provided from the PWM control unit 35, and therefore the voltages that correspond to the three-phase command voltage V_UVW* are applied to the U-phase stator coil 51, the V-phase stator coil 52 and the W-phase stator coil 53 of the motor 3.
The current deviation calculation unit 32 and the PI control unit 33 constitute a current feedback control unit. The current feedback control unit controls the electric current that is supplied to the motor 3 in such a manner that the electric current that is supplied to the motor 3 approaches the two-phase command current value I_γδ* that is set by the command current value preparation unit 30. FIG. 3 is a control block diagram of the electric power steering system. Note that the function of the addition angle limiter 24 is omitted to simplify the explanation.
Through the PI control (K_Pis a proportionality coefficient, K_Iis an integration coefficient, and l/s is an integration operator) on the deviation (torque deviation) ΔT of the control torque T from the command steering torque T*, the addition angle α is prepared. The present value θ_C(n) (θ_C(n)=θ_C(n−1)+α) of the control angle θc is obtained by adding the addition angle α to the immediately preceding value θ_C(n−1) of the control angle θ_C. At this time, the deviation of the actual rotor angle θ_Mof the rotor 50 from the control angle θ_Cis used as the load angle θ_L(θ_L=θ_C−θ_M).
Therefore, if the γ-axis current I_γ is supplied to the γ-axis (imaginary axis) in the γδ coordinate system (imaginary rotating coordinate system), which rotates in accordance with the control angle θ_C, based on the γ-axis command current value I_γ*, the q-axis current I_qis equal to I_γ sin θ_L(I_q=I_γ sin θ_L). The q-axis current I_qcontributes to generation of torque by the rotor 50. That is, the value obtained by multiplying the q-axis current I_q(=I_γ sin θ_L) by the torque constant K_Tof the motor 3 is transmitted to the steering mechanism 2 via the speed reduction mechanism 7 as the assist torque T_A(=K_T×I_γ sin θ_L). The value obtained by subtracting the assist torque T_Afrom a load torque from the steering mechanism 2 is the steering torque that should be applied by the driver to the steering wheel 10. When the steering torque is fed back through the steering torque limiter 20 and the detected steering torque correction unit 40, a system is operated in such a manner that the steering torque is brought to the command steering torque T*. That is, the addition angle α is obtained and the control angle θ_Cis controlled based on the addition angle α so that the control torque T coincides with the command steering torque T*.
The control angle θ_Cis updated with the use of the addition angle α that is obtained based on the deviation ΔT of the control torque T from the command steering torque T* while an electric current is supplied to the γ-axis that is the imaginary axis used in the control. Thus, the load angle θ_Lchanges and therefore, the torque that corresponds to the load angle θ_Lis generated by the motor 3. Therefore, the torque that corresponds to the command steering torque T* set based on the steering angle and the vehicle speed is generated by the motor 3. Accordingly, an appropriate steering assist force that corresponds to the steering angle and the vehicle speed is applied to the steering mechanism 2. That is, a steering assist control is executed in such a manner that the steering torque increases as the absolute value of the steering angle increases and the steering torque decreases as the vehicle speed increases.
Therefore, there is provided the electric power steering system in which an appropriate steering assist operation is executed by appropriately controlling the motor 3 without using a rotational angle sensor. Thus, the configuration is simplified and cost is reduced. FIG. 8 is a flowchart for describing the function of the addition angle limiter 24. The addition angle limiter 24 compares the addition angle α obtained by the PI control unit 23 with the upper limit UL (step (hereinafter, referred to as “S”) 1). When the addition angle α is larger than the upper limit UL (“YES” in S1), the upper limit UL is substituted for the addition angle α (S2). Thus, the upper limit UL (=+ω_max) is added to the control angle θ_C.
When the addition angle α obtained by the PI control unit 23 is equal to or smaller than the upper limit UL (“NO” in S1), the addition angle limiter 24 further compares the addition angle α with the lower limit LL (S3). When the addition angle α is smaller than the lower limit LL (“YES” in S3), the lower limit LL is substituted for the addition angle α (S4). Thus, the lower limit LL (=−ω_max) is added to the control angle θ_C.
When the addition angle α obtained by the PI control unit 23 is equal to or larger than the lower limit LL and equal to or smaller than the upper limit UL (“NO” in S3), the addition angle α is added to the control angle θ_Cwithout limitation. Therefore, the addition angle limiter 24 limits the addition angle α to a value within the range between the upper limit UL and the lower limit LL so as to stabilize the control. More specifically, although the control state is unstable (assist force is unstable) when the electric current is low or when the control starts, the control is encouraged to move to the stable state.
In the embodiment described above, the detected steering torque correction unit 40 is provided. When the absolute value |T_L| of the detected steering torque T_Lis equal to or smaller than the predetermined value a (|T_L|≦a), the detected steering torque correction unit 40 corrects the detected steering torque to 0. On the other hand, when the absolute value |T_L| of the detected steering torque T_Lis larger than the predetermined value a (|T_L|>a), the detected steering torque correction unit 40 outputs the detected steering torque T_Lwithout correction. If the detected steering torque correction unit 40 is not provided, the following problem may occur. When the steering wheel 10 is in the neutral position, the detected steering angle detected by the steering angle sensor 4 becomes 0. Therefore, the command steering torque T* set by the command steering torque setting unit 21 becomes 0 Nm as shown in FIG. 4. In the case where the driver takes his/her hands off the steering wheel 10 when the steering wheel 10 is in a position near the neutral position, if the steering torque detected by the torque sensor 1 has an error, the steering torque detected by the torque sensor 1 does not become 0 Nm. Accordingly, the torque deviation ΔT calculated by the torque deviation calculation unit 22 does not become 0. Therefore, the control angle θ_Cchanges. Then, the torque (assist torque) of the motor 3 changes, and therefore a steering force is supplied to the steering mechanism 2.
That is, when the detected steering torque correction unit 40 is not provided, if the driver takes his/her hands off the steering wheel 10 when the steering wheel 10 is in a position near the neutral position, self-steering may be performed, that is, the steered wheels may be steered by the steering mechanism 2. In the embodiment described above, when the driver takes his/her hands off the steering wheel 10 when the steering wheel 10 is in a position near the neutral position, even if the detected steering torque detected by the torque sensor 1 does not become 0 Nm, the detected steering torque detected by the torque sensor 1 is corrected to 0 Nm by the detected steering torque correction unit 40. Thus, the torque deviation ΔT calculated by the torque deviation calculation unit 22 becomes 0, and therefore, the control angle θ_Cdoes not change. According to the embodiment described above, it is possible to prevent occurrence of self-steering when the driver takes his/her hands off the steering wheel 10 when the steering wheel 10 is in a position near the neutral position.
With the detected steering torque correction unit 40, when the detected steering torque T_Loutput from the torque limiter 20 changes so as to exceed the predetermined value a or changes so as to fall below the predetermined value −a, the control torque T output from the detected steering torque correction unit 40 changes sharply, as shown in FIG. 6. Then, the steering torque also changes sharply, which may deteriorate the steering feel. Therefore, a unit that has the input-output characteristics as shown in FIG. 9 may be used as the detected steering torque correction unit 40. More specifically, when the absolute value |T_L| of the detected steering torque T_Lis equal to or smaller than the first predetermined value a (a>0) (|T_L|≦a), the detected steering torque correction unit 40 corrects the detected steering torque T_Lto 0. When the detected steering torque T_Lis higher than the first predetermined value a and lower than the second predetermined value b that is higher than the first predetermined value a (b>a) (a<T_L<b), the detected steering torque correction unit 40 corrects the detected steering torque T_Lin such a manner that the output value T smoothly increases (linearly changes in an example in FIG. 9) from a value near 0 as the detected steering torque T_Lbecomes higher than the predetermined value a by a larger amount. When the detected steering torque T_Lis equal to or higher than the second predetermined value b, the detected steering torque correction unit 40 outputs the detected steering torque T_Lwithout correction.
When the detected steering torque T_Lis lower than the predetermined value −a and higher than the predetermined value −b (−b<T_L<−a), the detected steering torque correction unit 40 corrects the detected steering torque T_Lin such a manner that the output value T smoothly decreases from a value near 0 (linearly changes in the example in FIG. 9) as the detected steering torque T_Lbecomes lower than the predetermined value −a by a larger amount. When the detected steering torque T_Lis equal to or lower than the predetermined value −b, the detected steering torque correction unit 40 outputs the detected steering torque T_Lwithout correction.
The first predetermined value a is set to, for example, a value within a range from 0.3 Nm to 0.5 Nm. The second predetermined value b is set to, for example, a value that is equal to or lower than the maximum torque that can be detected by the torque sensor 1 (the maximum torque immediately before the output from the torque sensor 1 is saturated). More specifically, the second predetermined value b is set to a value equal to or lower than the above-described upper limit saturation value +T_max(see FIG. 5).
That is, the detected steering torque correction unit 40 calculates the control torque T based on Equations 7-1 to 7-5. Note that, when the second predetermined value b is set to a value equal to the upper limited saturation value, correction based on Equations 7-3 to 7-5 is not required.
If −a≦T _L ≦a, then T=0 Equation 7-1
If a<T _L <b, then T={b/(b−a)}×T _L −{ab/(b−a)} Equation 7-2
If T_L≧b, then T=T_L Equation 7-3
If −b<T _L <−a, then T={b/(b−a)}×T _L +{ab/(b−a)} Equation 7-4
If T _L ≦−b, then T=T _L Equation 7-5
More specifically, a map that corresponds to the input-output characteristics as shown in FIG. 9 is prepared in advance according to Equations 7-1 to 7-5. The detected steering torque correction unit 40 corrects the detected steering torque based on the map. If the detected steering torque correction unit 40 is used, even if the detected steering torque T_Loutput from the torque limiter 20 changes so as to exceed the predetermined value a or changes so as to fall below the predetermined value −a, the control torque T calculated by the detected steering torque correction unit 40 smoothly changes. Therefore, the steering feel improves. In the example in FIG. 9, the map is formed of functions that are continuous with each other at each point at which the absolute value of the detected steering torque T_Lis equal to the second predetermined value b. Alternatively, as shown in FIG. 10, the map may be formed of functions that are not continuous with each other at each point at which the absolute value of the detected steering torque T_Lis equal to the second predetermined value b.
In the example in FIG. 9, when the detected steering torque T_Lis higher than the first predetermined value a and lower than the second predetermined value b (a<T_L<b) or when the detected steering torque T_Lis lower than the predetermined value −a and higher than the predetermined value −b (−b<T_L<−a), the input-output characteristics of the detected steering torque correction unit 40 changes in such a manner that the absolute value of the control torque T smoothly and linearly increases from a value near 0 as the absolute value of the detected steering torque T_Lincreases. Alternatively, the input-output characteristics of the detected steering torque correction unit 40 may change in such a manner that the absolute value of the control torque T smoothly and non-linearly increases from a value near 0 as the absolute value of the detected steering torque T_Lincreases.
While the embodiment of the invention has been described, the invention is not limited to the above-described embodiment and may be implemented in various other embodiments. For example, in the embodiment described above, the addition angle α is obtained by the PI control unit 23. The addition angle α may be obtained by a PID (proportional-integral-differential) calculation unit instead of the PI control unit 23. In the embodiment described above, a rotational angle sensor is not provided and the motor 3 is driven by executing the sensorless control. Alternatively, a rotational angle sensor, for example, a resolver may be provided and the above-described sensorless control may be executed when the rotational angle sensor malfunctions. Thus, even if the rotational angle sensor malfunctions, driving of the motor 3 is continued. Therefore, the steering assist operation is continued.
In this case, when the rotational angle sensor is used, the δ-axis command current value I_δ* may be prepared by the command current value preparation unit 30 based on the steering torque and the vehicle speed and according to the predetermined assist characteristics. In the embodiment described above, the invention is applied to the electric power steering system. Alternatively, the invention may be applied to a motor control for an electric pump hydraulic power steering system. Further alternatively, the invention may be implemented in various embodiments other than a control of a motor for an electric pump hydraulic power steering system and a power steering system. For example, the invention may be applied to a steer-by-wire (SBW) system, a variable gear ratio (VGR) steering system, and a control of a brushless motor provided in another type of vehicle steering system. The motor control unit according to the invention may be used in not only a control for the vehicle steering system but also controls for motors for other use.
In addition, various design changes may be made within the scope of claims.

Claims

1. A motor control unit that controls a motor that includes a rotor and a stator that faces the rotor, comprising:

a current drive unit that drives the motor based on an axis current value of a rotating coordinate system that rotates in accordance with a control angle that is a rotational angle used in a control;

an addition angle calculation unit that calculates an addition angle that is to be added to the control angle;

a control angle calculation unit that obtains a present value of the control angle by adding the addition angle calculated by the addition angle calculation unit to an immediately preceding value of the control angle in predetermined calculation cycles;

a control torque calculation unit that calculates a control torque based on a torque that is other than a motor torque and that is applied to a drive target that is driven by the motor; and

a command torque setting unit that sets a command torque that is a torque that is other than the motor torque and that is to be applied to the drive target, wherein

the addition angle calculation unit calculates the addition angle based on a deviation of the control torque calculated by the control torque calculation unit from the command torque set by the command torque setting unit.

2. The motor control unit according to claim 1, wherein when an absolute value of the torque other than the motor torque is equal to or smaller than a first predetermined value, the control torque calculation unit sets the control torque to 0.

3. The motor control unit according to claim 2, wherein in a case where the torque other than the motor torque, which is input in the control torque calculation unit, is expressed by T_L, the first predetermined value is expressed by a, and a second predetermined value that is larger than the first predetermined value is expressed by b, the control torque calculation unit calculates the control torque such that, when a<T_L<b or −b<T_L<−a, an absolute value of the control torque linearly and smoothly increases from a value near 0 as the absolute value of the torque other than the motor torque increases.

4. The motor control unit according to claim 3, wherein when a<T_L<b, the control torque calculation unit calculates the control torque according to an equation, T={b/(b−a)}×T_L−{ab/(b−a)}, and when −b<T_L<−a, the control torque calculation unit calculates the control torque according to an equation, T={b/(b−a)}×T_L+{ab/(b−a)}.

5. The motor control unit according to claim 4, wherein when T_L≧b or T_L≦b, the control torque calculation unit sets the control torque to the torque other than the motor torque.

6. The motor control unit according to claim 2, wherein in a case where the torque other than the motor torque, which is input in the control torque calculation unit, is expressed by T_L, the first predetermined value is expressed by a, and a second predetermined value that is larger than the first predetermined value is expressed by b, the control torque calculation unit calculates the control torque such that, when a<T_L<b or −b<T_L<−a, an absolute value of the control torque non-linearly and smoothly increases from a value near 0 as the absolute value of the torque other than the motor torque increases.

7. A vehicle steering system, comprising:

a motor that supplies a driving force to a steering mechanism of a vehicle; and

the motor control unit according to claim 1.